Rerate Specification Date - EagleiTechnologies.com

1 Rerate Specification Date 5/09/2012. Client: ACME Chemical Report No.: Vessel: ACAX 80005. Contact: John Smith Phone No.: 555-836-2223 Year Built: 1970. EXECUTIVE SUMMARY. The Delaware Plant Reliability Engineer at ACME Chemicals in Claymont, DE requested Eagle Inspection Technologies to include Rerate calculations with the inspection report to support the proposed Rerate for the DOT Railcar ACAX 80005 to be set on stationary supports and continue in service as a stationary pressure vessel in Fluosulfonic Acid service. This request was due to the requirements of the PA Dept. of Labor and Industry for pressure vessels operating within their jurisdiction. The calculations contained herein were based on the client request to Rerate the vessel to 25psig at 200 F.

2 A corrosion allowance was established to meet MDMT requirements without impact testing and to extend the life of the vessel for greater than 20 years at the present estimated corrosion rate. All conditions appear to be satisfactory for the proposed Rerate of the Railcar ACAX 80005. Rerate must be performed in accordance with the latest revision of the National Board (NB) by a contractor that is a NB certified R stamp holder for repairs of pressure vessels. A Rerate nameplate must be install on the vessel and the PSV must be reset to 25psi maximum for over pressure protection of the vessel. Original Design Parameters Current Design Parameters Status MAWP No Reference MAWP 25psi Rerate change from original design Temp No Reference Temp 200'F Rerate change from original design MDMT No Reference MDMT -20'F Evaluation ASME S8 D1, UCS 66.

3 Confirms MDMT at -20 F. Ca No Reference Ca " Established to base remaining life to >20. years, 3/8" for all components Hydro Test Orig 400psi Hydro Test 33psi Hydro test required due to change from critical service (class 5 corrosive medium). Appendix A Vessel Rerate Engineering Calculations Appendix B Drawings Appendix C Supplemental Supporting Documents Appendix D Manufacturers Data Sheets Project No.: Author: Jeff Walling Page 1 of 9. Page 1. Appendix A. Vessel Rerate Engineering Calculations 1) Cylindrical Shell Calculations 2) Formed Head Calculations 3) Nozzle Calculations 4) Nozzle Reinforcement Calculations 5) Horizontal Vessel Stress Calculations 6) Component MDMT Evaluation 7) Component Stress Calculations Project No.: Author: Jeff Walling Page 2 of 49.

4 Page 2. PRESSURE VESSEL CYLINDRICAL SHELL CALCULATIONS Date ASME SECTION VIII, Div 1, UG-27_28 5/9/2012. Client: ACME Chemical Project No.: Vessel ACAX 80005 Component Main Shell Material AAR-TC128-B. MAWP Prod. SG Temp. tnom Do Ca Year Built 25 200 1970. Int. Pressure Min. Thickness Calcs PR/( ) = t (> tx or PR/( ) = tr). P 33 Design Pressure, psi S 23100 Stress, psi R Inside Radius, in. t Minimum Thickness, in. E Joint Efficiency tr t for Reinf. Calc External Pressure Minimum Thickness Calculation L Effective Length, in. A Factor from Figure G. Do Outside Diameter, in. B Stress Value L/Do Pa External Pressure, psi X-Chart Do/t tx Minimum Thickness, in. Internal Pressure Calculation SEt/(R+ ) = P. t = tnom - Ca = Thickness, in. P Internal Pressure, psi External Pressure Calculation t Thickness, in.

5 A Factor from Figure G. L/Do B Stress Value X-Chart Do/t Pa External Pressure Variables for Capacities Cylinder Capacities Shell Length, in. lb's of Prod lb's of Shell Radius, in Cu Ft Gals Water Prod. Shell Thickness, in 3104 23217 193562 356155. Plate Data Total lb's Metal lb's of Sq In Sq Ft Cu in Steel Prod + Steel 178694 1242 130804 37061 393215. Project No.: Author: JLW Page 1 of 1. Page 3. PRESSURE VESSEL ELLIPSOIDAL HEAD CALCULATIONS Date ASME SECTION VIII, Div 1, UG-32_33 5/9/2012. Client: ACME Chemical Project No.: MAWP 25. Vessel ACAX80005 Component Head 1&2 Material AAR-TC128-B Ca Int. Press. Min. t Calcs (Knl) PD/( ) = t & (Cntrl) ( )=t (2:1 Ellipsoidal). P Design Pressure, psi E Joint Efficiency T 200 Design Temperature, F S 23100 Stress, psi D Inside Diameter, in.

6 K_K1 factor(s) (D/2H). tnom Nominal Thickness, in. CP Central Portion, in. h Inside Head Height, in. t Min. Thickness, in. (Knl). Static Head, ft t Min. Thickness, in. (Cntrl). External Pressure Minimum Thickness Calculation B/(Ro/t) = Pa Ro A Factor from Figure G. X-Chart B Stress Value Do Ho Do/2Ho Ko Pa External Pressure, psi t Minimum Thickness, in. Internal Pressure Calculation 2 SEt/(D+ ) = P. t = tnom -Ca = Thickness, in. P Internal Pressure, psi External Pressure Calculation B/(Ro/t) = Pa t Thickness, in. A Factor from Figure G. Ro X-Chart B Stress Value Pa External Pressure, psi. Variables for Capacities (Includes 2 inch head skirt width) Total lb's t Nominal thickness, in. Rm Mean Radius, in. Prod + Steel hm Mean Head Height, in. Pel Head Perimeter, in.

7 19005. Head Capacities Plate Data lb's of Prod lb's of Metal lb's of Cu Ft Gals Water Prod. Sq In Sq Ft Cu in Steel 131 979 8163 15020 18009 125 14065 3985. Project No.: Author.: JLW Page 1 of 1. Page 4. PRESSURE VESSEL NOZZLE CALCULATIONS Date 5/9/2012. ASME S8 D1, UG-27_45 Year Built ClienW ACME Chemical Project No.: Vessel ACAX 80005 1970. Comp. Manway Noz. Type Boss Flange Material CS - A105. MAWP Prod. SG Temp. tnom Size Do Ca 25 200 5 28 28 Int. Pressure Min. Thickness Calc PR/( ) = t P Design Pressure, psi S 20000 Stress, psi 04. R Inside Radius, in. t Calculated t, in. E Joint Efficeincy Attaching Component tmin = Minimum Design t = Standard Pipe - = Minimum Required Thickness = External Pressure Minimum Thickness Calculation L Effective Length, in.

8 A Factor from Figure G. Do Outside Diameter, in. B Stress Value L/Do Pa External Pressure, psi X-Chart Do/t t Minimum Thickness, in. Internal Pressure Calculation SEt/(R+ ) = P. t = tnom - Ca = Thickness, in. P Internal Pressure, psi External Pressure Calculation t Thickness, in. A Factor from Figure G. L/Do B Stress Value X-Chart Do/t Pa External Pressure Variables for Capacities Cylinder Capacities Shell Length, in. lb's of Prod lb's of Shell Radius, in. Cu Ft Gals Water Prod. Shell Thickness, in 1 4 33 61. Plate Data Metal lb's of NOTE: Total lb's Sq In Sq Ft Cu in Steel Flange Weight Prod + Steel 186 1 838 237 Not Considered 298. Project No.: Author: JLW Page 1 of 1. Page 5. PRESSURE VESSEL NOZZLE REINFORCEMENT CALCULATIONS. ASME S8, D1 UG-37.

9 Date Client: $&0( &KHPLFDO Project No.: 5/9/2012. Vessel ACAX 80005 Pressure 25 psi Temperature 200 F. Nozzle Without Reinforcing Element Component Vessel Material Nozzle Material tr based on: Manway AAR-TC128-B CS - A105 Internal Pressures Do t nom Cv tn nom Cn Confg. 1=Butt, d E Rn Sv Sn 2=thru, 3 3 = Ext. 23100 20000. Fr1 Fr2 F t tr tn trn t1 t2 h ti 1 A Area Required = dtrF + 2tntrF(1 - fr1) Nozzle Groove Weld? Yes t= A1 Area available in shell, in.^2 (use larger value). Element Groove Weld? A1a = d(Et - Ftr) - 2tn(Et - Ftr)(1 - fr1). No t= A1b = 2(t + tn)(Et - Ftr) - 2tn(Et - Ftr)(1 - fr1). A2 Area avail. in nozzle projecting outward, in.^2 (use smaller value). A2a = 5(tn - trn)fr2t A2b = 5(tn - trn)fr2tn A3 Area available in inward nozzle, in.)

10 ^2 (use smaller value). A3a = 5ttifr2. A3b = 5titifr2. A3c = 2htifr2. A41 Area available in outward weld, in.^2 = t12fr2. A43 Area available in inward weld, in.^2 = t22fr2. Total Area Available, in.^2 = (A1 + A2 + A3 + A41 + A43). Sufficient Reinforcement Project No.: Author.: JLW Page 1 of 3. Page 6. Nozzle With Reinforcing Element Reinforcement Limit, in. = Pad Material: CS Unknown Dp te Sp Fr3 Fr4 t1 t3. 13800 A Area Required, in.^2 = dtrF + 2tntrF(1 - fr1). A1 Area available in shell, in.^2 (use larger value). A1a = d(Et - Ftr) - 2tn(Et - Ftr)(1 - fr1). A1b = 2(t + tn)(Et - Ftr) - 2tn(Et - Ftr)(1 - fr1). A2 Area avail. in nozzle projecting outward, in.^2 (use smaller value). A2a = 5(tn - trn)fr2t A2c = 5(tn - trn)fr2t( + te)fr2. A3 Area available in inward nozzle, in.